US20160290492A1 - Planetary carrier - Google Patents
Planetary carrier Download PDFInfo
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- US20160290492A1 US20160290492A1 US15/035,260 US201415035260A US2016290492A1 US 20160290492 A1 US20160290492 A1 US 20160290492A1 US 201415035260 A US201415035260 A US 201415035260A US 2016290492 A1 US2016290492 A1 US 2016290492A1
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- portions
- pinion gears
- bridge portions
- oil
- planetary carrier
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/08—General details of gearing of gearings with members having orbital motion
- F16H57/082—Planet carriers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/62—Gearings having three or more central gears
- F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
- F16H3/663—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another with conveying rotary motion between axially spaced orbital gears, e.g. RAVIGNEAUX
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/042—Guidance of lubricant
- F16H57/043—Guidance of lubricant within rotary parts, e.g. axial channels or radial openings in shafts
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/0467—Elements of gearings to be lubricated, cooled or heated
- F16H57/0473—Friction devices, e.g. clutches or brakes
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/0467—Elements of gearings to be lubricated, cooled or heated
- F16H57/0479—Gears or bearings on planet carriers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/048—Type of gearings to be lubricated, cooled or heated
- F16H57/0482—Gearings with gears having orbital motion
- F16H57/0484—Gearings with gears having orbital motion with variable gear ratio or for reversing rotary motion
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/08—General details of gearing of gearings with members having orbital motion
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
- F16H2200/006—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising eight forward speeds
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
- F16H2200/2007—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with two sets of orbital gears
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
- F16H2200/2046—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with six engaging means
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
- F16H2200/2048—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with seven engaging means
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
- F16H2200/2066—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes using one freewheel mechanism
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/2079—Transmissions using gears with orbital motion using freewheel type mechanisms, e.g. freewheel clutches
- F16H2200/2082—Transmissions using gears with orbital motion using freewheel type mechanisms, e.g. freewheel clutches one freewheel mechanisms
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Details Of Gearings (AREA)
- Structure Of Transmissions (AREA)
Abstract
A planetary carrier where the second pinion gears are disposed so as to be at least partially located in the spaces between the adjacent bridge portions, an outer peripheral surface of each of the bridge portions is provided with a spline onto which a friction engagement plate constituting a friction engagement element is fitted, an inner peripheral surface of each of the bridge portions is provided with a pair of wall portions that extend in the axial direction along side edges on both sides of each of the bridge portions and protrude radially inward, and each of the bridge portions is provided with a plurality of oil holes through which an inside and an outside of each of the bridge portions communicate with each other.
Description
- The present disclosure relates to a planetary carrier of a planetary gear including first and second pinion gears having axial lengths different from each other.
- Conventionally, as a planetary carrier of this type, a planetary carrier has been known which rotatably supports short pinion gears and long pinion gears of a Ravigneaux type planetary gear constituting a transmission (see Japanese Patent Application Publication No. 2008-089051, for example). This planetary carrier includes a carrier body and a carrier cover, and the carrier cover has an annular extension portion that surrounds the substantially entire short pinion gears and portions of the long pinion gears. The extension portion of the carrier cover constitutes a clutch hub of a clutch (C-2) that is disposed to surround the extension portion. On the outer peripheral side of a drum portion of the carrier body, a brake (B-2) and a one-way clutch (F-1) are arranged side by side,
- In the conventional planetary carrier described above, because the extension portion of the carrier cover is formed so as to surround the short pinion gears and portions of the long pinion gears, the outer diameter of the carrier cover tends to be larger, which makes it difficult to make the planetary carrier compact to improve the space efficiency in the transmission. When the planetary carrier functions as a hub of a friction engagement element such as a clutch as described above, hydraulic oil as a lubricating medium is required to be sufficiently supplied to friction engagement plates supported by the planetary carrier as a hub,
- In view of this, an exemplary aspect of the present disclosure makes a compact planetary carrier which rotatably supports first and second pinion gears having axial lengths different from each other and onto which friction engagement plates of a friction engagement element are fitted, and to make it possible to sufficiently supply a lubricating medium to the friction engagement plates.
- A planetary carrier according to an exemplary aspect of the present disclosure is planetary carrier of a planetary gear including a plurality of first pinion gears and a plurality of second pinion gears having longer axial lengths than those of the first pinion gears, the planetary carrier including: a carrier body including a plurality of first shaft support portions that each support one end of a first pinion shaft inserted into each of the first pinion gears, and also including a plurality of second shaft support portions that are arranged alternately with the first shaft support portions along a circumferential direction and each support one end of a second pinion shaft inserted into each of the second pinion gears; a carrier cover that supports the other end of the first pinion shaft and the other end of the second pinion shaft; and a plurality of bridge portions that extend in an axial direction of the first and the second pinion shafts between the first shaft support portions and the carrier cover, and are arranged side by side in the circumferential direction with spaces between the bridge portions, in which the second pinion gears are disposed so as to be at least partially located in the spaces between the adjacent bridge portions, an outer peripheral surface of each of the bridge portions is provided with a spline onto which a friction engagement plate constituting a friction engagement element is fitted, an inner peripheral surface of each of the bridge portions is provided with a pair of wall portions that extend in the axial direction along side edges on both sides of each of the bridge portions and protrude radially inward, and each of the bridge portions is provided with a plurality of oil holes through which an inside and an outside of each of the bridge portions communicate with each other.
- As in this planetary carrier, the bridge portions are provided so as to be arranged side by side in the circumferential direction between the first shaft support portions of the carrier body and the carrier cover, and the second pinion gears are disposed so as to be at least partially located in the spaces between the adjacent bridge portions, whereby the outer diameter (occupied space) of the planetary carrier around the bridge portions can be reduced. In this planetary carrier, the carrier cover and the inner peripheral surface and the pair of wall portions of each of the bridge portions define an oil accumulating portion that stores hydraulic oil scattered from the inside (axis side). Thus, the hydraulic oil scattered from the inside can be stored inside the bridge portions so as to be prevented from being discharged outside through the spaces, and then the hydraulic oil as a lubricating medium can be supplied through the oil holes to the friction engagement plate fitted onto the spline. Consequently, while making the planetary carrier of the planetary gear including the first and the second pinion gears having axial lengths different from each other compact, it is possible to sufficiently supply hydraulic oil as a lubricating medium to the friction engagement plate supported by the bridge portions.
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FIG. 1 is a schematic structure diagram illustrating a power transmission apparatus including a Ravigneaux type planetary gear having a planetary carrier according to the present disclosure. -
FIG. 2 is an operation table illustrating a relation between shift speeds and operating states of clutches and brakes of a transmission included in the power transmission apparatus in theFIG. 1 . -
FIG. 3 is a partial sectional view illustrating a main part of the automatic transmission included in the power transmission apparatus. -
FIG. 4 is a perspective view illustrating a carrier body constituting the planetary carrier of the Ravigneaux type planetary gear included in the power transmission apparatus inFIG. 1 . -
FIG. 5 is a schematic diagram illustrating the Ravigneaux type planetary gear included in the power transmission apparatus inFIG. 1 . -
FIG. 6 is a sectional view illustrating an oil receiver attached to the planetary carrier of the Ravigneaux type planetary gear included in the power transmission apparatus inFIG. 1 . -
FIG. 7 is a front view of the oil receiver inFIG. 6 when viewed from a sliding surface side. -
FIG. 8 is a schematic diagram for describing oil grooves formed on the sliding surface of the oil receiver inFIG. 6 . -
FIG. 9 is a sectional view along line A-A inFIG. 7 . -
FIG. 10 is a sectional view along line B-B inFIG. 7 . -
FIG. 11 is a front view of an oil receiver according to another embodiment when viewed from a sliding surface side. -
FIG. 12 is a sectional view for describing oil grooves formed on the sliding surface of the oil receiver inFIG. 11 . - Modes for carrying out the present disclosure will now be described with reference to the accompanying drawings.
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FIG. 1 is a schematic structure diagram illustrating apower transmission apparatus 20 including a Ravigneaux type planetary gear having a planetary carrier according to the present disclosure. Thepower transmission apparatus 20 shown inFIG. 1 is an apparatus that is connected to a crankshaft of an engine (not shown) mounted on a front-wheel-drive vehicle, and can transmit power from the engine to right and left drive wheels (front wheels) (not shown). As shown in the figure, thepower transmission apparatus 20 includes atransmission case 22, a starting device (fluid transmission apparatus) 23 accommodated in thetransmission case 22, anoil pump 24, anautomatic transmission 25, a gear mechanism (gear train) 28, and a differential gear (differential mechanism) 29. - The
starting device 23 included in thepower transmission apparatus 20 is structured as a torque converter including: apump impeller 23 p on the input side connected to a crankshaft of the engine; aturbine runner 23 t on the output side connected to an input shaft (input member) 26 of theautomatic transmission 25; astator 23 s that is disposed inside thepump impeller 23 p and theturbine runner 23 t to rectify a flow of hydraulic oil (ATF, i.e., oil) from theturbine runner 23 t to thepump impeller 23 p; a one-way clutch 23 o that restricts the rotation direction of thestator 23 s to one direction; alockup clutch 23 c; and adamper mechanism 23 d. However, thestarting device 23 may be structured as a fluid coupling that does not have thestator 23 s. - The
oil pump 24 is structured as a gear pump including: a pump assembly including a pump body and a pump cover; an external gear connected to thepump impeller 23 p of thestarting device 23 via a hub; and an internal gear meshing with the external gear. Theoil pump 24 is driven by power from the engine, sucks hydraulic oil stored in an oil pan (not shown), and pressure-feeds the hydraulic oil to a hydraulic control apparatus (not shown) that generates an oil pressure required by thestarting device 23 and theautomatic transmission 25. - The
automatic transmission 25 is structured as an eight-speed transmission. As shown inFIG. 1 , in addition to theinput shaft 26, theautomatic transmission 25 includes: a firstplanetary gear mechanism 30 of a double-pinion type; a secondplanetary gear mechanism 35 of a Ravigneaux type; and four clutches C1, C2, C3, and C4, two brakes B1 and B2, and a one-way clutch F1 that are configured to change power transfer paths from the input side to the output side. - The first
planetary gear mechanism 30 of theautomatic transmission 25 has: asun gear 31 that is an external gear; aring gear 32 that is an internal gear disposed concentrically with thissun gear 31; and aplanetary carrier 34 rotatably (turnably) and revolvably holding a plurality sets of twopinion gears sun gear 31 and the other of which meshes with thering gear 32. As shown in the figure, thesun gear 31 of the firstplanetary gear mechanism 30 is fixed to thetransmission case 22, and theplanetary carrier 34 of the firstplanetary gear mechanism 30 is coupled to theinput shaft 26 so as to be rotatable together with theinput shaft 26, The firstplanetary gear mechanism 30 is structured as what is called a reduction gear, and reduces the speed of power transmitted to theplanetary carrier 34 being an input element to output the power from thering gear 32 being an output element. - The second
planetary gear mechanism 35 of theautomatic transmission 25 has: afirst sun gear 36 a and asecond sun gear 36 b that are external gears; aring gear 37 that is an internal gear disposed concentrically with the first and thesecond sun gears short pinion gears 38 a meshing with thefirst sun gear 36 a; a plurality oflong pinion gears 38 b meshing with thesecond sun gear 36 b and theshort pinion gears 38 a and also meshing with thering gear 37; and aplanetary carrier 40 rotatably (turnably) and revolvably holding theshort pinion gears 38 a and thelong pinion gears 38 b. Thering gear 37 of the secondplanetary gear mechanism 35 functions as an output member of theautomatic transmission 25, and power transmitted from theinput shaft 26 to thering gear 37 is transmitted to right and left drive wheels via thegear mechanism 28, thedifferential gear 29, and a drive shaft. Theplanetary carrier 40 is supported by thetransmission case 22 via the one-way clutch F1, and the rotation direction of theplanetary carrier 40 is restricted to one direction by the one-way clutch F1. - The clutch C1 is a multi-plate friction type hydraulic clutch (friction engagement element) that has a piston, a plurality of friction plates and separator plates, and a hydraulic servo including an oil chamber to which hydraulic oil is supplied, and can connect and disconnect the
ring gear 32 of the firstplanetary gear mechanism 30 to and from thefirst sun gear 36 a of the secondplanetary gear mechanism 35. The clutch C2 is a multi-plate friction type hydraulic clutch that has a piston, a plurality of friction plates and separator plates, and a hydraulic servo including an oil chamber to which hydraulic oil is supplied, and can connect and disconnect theinput shaft 26 to and from theplanetary carrier 40 of the secondplanetary gear mechanism 35. The clutch C3 is a multi-plate friction type hydraulic clutch that has a piston, a plurality of friction plates and separator plates, and a hydraulic servo including an oil chamber to which hydraulic oil is supplied, and can connect and disconnect thering gear 32 of the firstplanetary gear mechanism 30 to and from thesecond sun gear 36 b of the secondplanetary gear mechanism 35. The clutch C4 is a multi-plate friction type hydraulic clutch that has a piston, a plurality of friction plates and separator plates, and a hydraulic servo including an oil chamber to which hydraulic oil is supplied, and can connect and disconnect theplanetary carrier 34 of the firstplanetary gear mechanism 30 to and from thesecond sun gear 36 b of the secondplanetary gear mechanism 35. - The brake B1 is a multi-plate friction type hydraulic brake that has a plurality of friction plates and separator plates and a hydraulic servo including an oil chamber to which hydraulic oil is supplied, and can hold the
second sun gear 36 b of the secondplanetary gear mechanism 35 stationary to thetransmission case 22 and can also release thesecond sun gear 36 b held stationary with respect to thetransmission case 22. The brake B2 is a multi-plate friction type hydraulic brake that has a plurality of friction plates and separator plates and a hydraulic servo including an oil chamber to which hydraulic oil is supplied, and can hold theplanetary carrier 40 of the secondplanetary gear mechanism 35 stationary to thetransmission case 22 and can also release theplanetary carrier 40 held stationary with respect to thetransmission case 22, - The one-way clutch F1 is a clutch that includes an inner race coupled (fixed) to the
planetary carrier 40 of the secondplanetary gear mechanism 35, an outer race, a plurality of sprags, a plurality of springs (leaf springs), and a retainer, and that transmits torque via the respective sprags when the outer race rotates in one direction with respect to the inner race, and also allows both of the races to relatively rotate when the outer race rotates in the other direction with respect to the inner race. However, the one-way clutch F1 may have a roller-type structure, for example, other than the sprag-type. - The clutches C1 to C4 and the brakes B1 and B2 operate with hydraulic oil supplied and discharged by the hydraulic control apparatus described above.
FIG. 2 is an operation table illustrating a relation between shift speeds and operating states of the clutches C1 to C4, the brakes B1 and B2, and the one-way clutch F1 of theautomatic transmission 25. Theautomatic transmission 25 controls the clutches C1 to C4 and the brakes B1 and B2 to achieve the states specified in the operation table inFIG. 2 , thereby providing shift speeds of first to eighth forward speeds and shift speeds of first and second reverse speeds. Herein, at least any of the clutches C1 to C4 and the brake B2 except the brake B1 may be an intermeshing engagement element such as a dog clutch. -
FIG. 3 is a partial sectional view illustrating a main part of theautomatic transmission 25 included in thepower transmission apparatus 20. This drawing illustrates a structure around the clutch C2 of theautomatic transmission 25 and the secondplanetary gear mechanism 35 of the Ravigneaux type. - As shown in
FIG. 3 , the clutch C2 that is disposed near theplanetary carrier 40 and connects and disconnects theplanetary carrier 40 to and from theinput shaft 26 includes: aclutch drum 200; a plurality of separator plates (friction engagement plates) 201 and a backing plate; friction plates (friction engagement plates) 202 disposed alternately with theseparator plates 201, for example; apiston 203; and a cancel plate (cancel oil-chamber defining member) 204. Theclutch drum 200 is fixed to theinput shaft 26 as a power input member to rotate together with theinput shaft 26. Theseparator plates 201 are annular members both surfaces of which are smoothly formed and, together with the backing plate, are fitted onto splines formed on the inner peripheral surface of theclutch drum 200. Thefriction plates 202 are annular members on both surfaces of which friction materials are bonded. - The
piston 203 is movably supported by an inner tubular portion (not shown) of theclutch drum 200, and together with theclutch drum 200 defines an engagement oil chamber (not shown). To the engagement oil chamber, engagement oil pressure (hydraulic oil) for engaging the clutch C2 is supplied from a hydraulic control apparatus (not shown) through an oil passage, for example, formed in theinput shaft 26. Oil pressure in the engagement oil chamber acts on thepiston 203, so that thepiston 203 is moved in the axial direction of theinput shaft 26 to press theseparator plates 201 and thefriction plates 202, whereby the clutch C2 is engaged. The cancelplate 204 together with thepiston 203 defines a cancel oil chamber for canceling centrifugal oil pressure generated in the engagement oil chamber. Between thepiston 203 and the cancelplate 204, a plurality of return springs are arranged at intervals in the circumferential direction. - The
planetary carrier 40 of the secondplanetary gear mechanism 35 includes acarrier body 41 in a substantially cylindrical shape and anannular carrier cover 42 that is fixed to thecarrier body 41, as shown inFIG. 3 andFIG. 4 . Thecarrier body 41 is formed by hot forging a metal, for example, and includes: an annularshaft support portion 410 that supports one end of each of a plurality of (four in the present embodiment)first pinion shafts 381 inserted into the correspondingshort pinion gear 38 a and one end of each of a plurality of (four in the present embodiment)second pinion shafts 382 inserted into the correspondinglong pinion gear 38 b; and a plurality of (four in the present embodiment)bridge portions 415 that extend from theshaft support portion 410 in the axial direction of the first and thesecond pinion shafts planetary carrier 40 and are arranged side by side in the circumferential direction with spaces G therebetween. - As shown in
FIG. 4 , theshaft support portion 410 has a center hole (circular hole) 411, formed in the center thereof, into which theinput shaft 26, thefirst sun gear 36 a, and thesecond sun gear 36 b of theautomatic transmission 25 are inserted, and also has a plurality of (four for each in the present embodiment) thick portions (first shaft support portions) 412 and plate-like thin portions (second shaft support portions) 413 that are arranged alternately (at 90° intervals in the present embodiment) around thecenter hole 411 along the circumferential direction. Thethick portions 412 are molded integrally with thethin portions 413 so as to be arranged side by side in the circumferential direction with spaces G therebetween. Each of thethick portions 412 is provided with ashaft hole 412 h into which one end of thefirst pinion shaft 381 inserted into the shaft hole of theshort pinion gear 38 a via aneedle bearing 383 is inserted. Each of thethin portions 413 is provided with ashaft hole 413 h into which one end of thesecond pinion shaft 382 inserted into the shaft hole of theshort pinion gear 38 a via aneedle bearing 384 is inserted. - Furthermore, in the present embodiment, each of the
bridge portions 415 extends from the outer peripheral portion of the distal end (upper end inFIG. 4 ) of each of thethick portions 412. Specifically, theshaft support portion 410 having thethick portions 412 and thethin portions 413 is molded integrally with thebridge portions 415, This makes it possible to appropriately secure the torsional rigidity of thecarrier body 41, and consequently the torsional rigidity of theplanetary carrier 40. As shown inFIG. 3 andFIG. 4 , therespective bridge portions 415 are formed so as to protrude radially outward of the shaft support portion 410 (the thick portions 412), and function as a clutch hub of the clutch C2 that connects and disconnects theplanetary carrier 40 to and from the input shaft 26 n, Specifically, on the outer peripheral surface of each of thebridge portions 415,splines 415 s are formed by cutting, for example. Onto thesplines 415 s, thefriction plates 202 constituting the clutch C2 are fitted. - The inner peripheral surface of each of the
bridge portions 415 is provided with a pair of (two)wall portions 415 w that extend along side edges on both sides of thebridge portion 415 in the axial direction of the first and thesecond pinion shafts planetary carrier 40. As shown inFIG. 4 , thewall portions 415 w protrude radially inward by a predetermined length from the side edges of each of thebridge portions 415. Thewall portions 415 w are molded simultaneously with each of thebridge portions 415 by hot forging, and the protruding lengths of thewall portions 415 w are determined such that thewall portions 415 w do not come in contact with the short pinion gears 38 a or the long pinion gears 38 b that are disposed inside thewall portions 415 w. As a result of forming such a pair ofwall portions 415 w, on each of thebridge portions 415, arecess 415 r is defined by the inner peripheral surface and the pair ofwall portions 415 w of thebridge portion 415. Furthermore, each of thebridge portions 415 is provided with a plurality ofoil holes 415 h at intervals. The oil holes 415 h provide communication between the inside and the outside of thebridge portion 415, and are open at the inner peripheral surface of thebridge portion 415 and bottom lands of thesplines 415 s. - The
carrier cover 42 is formed by performing press working on a metal plate, for example, in the present embodiment. Thecarrier cover 42 has: a center hole (circular hole) into which theinput shaft 26, for example, is inserted; a shaft hole into which the other end of thefirst pinion shaft 381 is inserted; and a shaft hole into which the other end of thesecond pinion shaft 382 is inserted. Thecarrier cover 42 is fixed to the distal ends (left end inFIG. 3 ) of thebridge portions 415 of thecarrier body 41 by welding, and foams a wall portion on the opposite side of thethick portions 412 via therecesses 415 r formed on thebridge portion 415. Thecarrier cover 42 supports the other end of each of thefirst pinion shafts 381 inserted into the shaft hole of the correspondingshort pinion gear 38 a via theneedle bearing 383, and also supports the other end of each of thesecond pinion shafts 382 inserted into the shaft hole of the correspondinglong pinion gear 38 b via theneedle bearing 384. - Accordingly, as shown in
FIG. 3 , the respective short pinion gears 38 a are disposed between thecarrier cover 42 and thethick portions 412 of the carrier body 41 (the shaft support portion 410) and inside (radially inward of) thebridge portions 415. As shown inFIG. 3 , the respective long pinion gears 38 b are disposed between thecarrier cover 42 and thethin portions 413 of the carrier body 41 (the shaft support portion 410). Furthermore, as shown inFIG. 5 , each of the long pinion gears 38 b meshes with the correspondingshort pinion gear 38 a, and is exposed outside through the space G of the planetary carrier 40 (the carrier body 41) to mesh with thering gear 37 that is disposed to surround thethick portions 412. Specifically, the respective long pinion gears 38 b are disposed so as to be at least partially located in the spaces G between theadjacent bridge portions 415 as shown inFIG. 5 . In other words, a portion of each of the long pinion gears 38 b is located within the range of radial thickness of thebridge portion 415. In this manner, the respective long pinion gears 38 b having long lengths are exposed outside through the spaces G of thecarrier body 41, whereby the outer diameter (occupied space) of theplanetary carrier 40 around therespective bridge portions 415 can be reduced. In the present embodiment, the respective long pinion gears 38 b are positioned radially inward of a circle (addendum circle of thesplines 415 s) circumscribing therespective bridge portions 415. Onto the ends of therespective bridge portions 415 of theplanetary carrier 40 on theshaft support portion 410 side, aninner race 100 of the one-way clutch F1 is press-fitted so as to surround thering gear 37, and is fixed by welding (seeFIG. 3 ). - To the
planetary carrier 40 of the secondplanetary gear mechanism 35 structured as described above, anoil receiver 50 that collects hydraulic oil scattered from theinput shaft 26 side (inside) in theplanetary carrier 40 is attached as shown inFIG. 3 . In the present embodiment, theoil receiver 50 is fixed to thecarrier cover 42 so as to be positioned between thecarrier cover 42 of theplanetary carrier 40 and the cancelplate 204 of the clutch C2. As shown inFIG. 6 , theoil receiver 50 includes an annularfirst plate member 51 disposed on thecarrier cover 42 side and an annularsecond plate member 52 that is integrated with thefirst plate member 51 by bonding, for example, and is disposed on the cancelplate 204 side. - The
first plate member 51 has a plurality of oil-collectingwalls 53 that extend in the extending direction (axial direction) of the axis (see the dashed and single-dotted line inFIG. 6 ) such that the oil-collectingwalls 53 protrude from the inner periphery toward the carrier cover 42 (right side inFIG. 6 ) at intervals in the circumferential direction. In the present embodiment, the oil-collectingwalls 53 are formed on thefirst plate member 51 at intervals in the circumferential direction so as to be prevented from coming into contact with the long pinion gears 3 8 b when theoil receiver 50 is attached to theplanetary carrier 40. However, when the oil-collectingwalls 53 are prevented from coming into contact with the long pinion gears 38 b, the oil-collectingwalls 53 may be formed in an annular shape along the inner periphery of thefirst plate member 51. - On the
first plate member 51, a plurality of (four for each in the present embodiment) first tubular portions (insertion portions) 55 and second tubular portions (insertion portions) 57 are formed so as to protrude toward the carrier cover 42 (right side inFIG. 6 ) in the extending direction of the axis. The first tubular portions (insertion portions) 55 each have anoil passage 55 a inside, and are arranged at intervals in the circumferential direction such that each of the firsttubular portions 55 can be inserted into an in-shaft axial oil passage (in-shaft oil passage) 381 a (seeFIG. 3 ) formed in the correspondingfirst pinion shaft 381. In the same manner, the second tubular portions (insertion portions) 57 each have anoil passage 57 a inside, and are arranged at intervals in the circumferential direction such that each of the secondtubular portions 57 can be inserted into an in-shaft axial oil passage (in-shaft oil passage) 382 a (seeFIG. 3 ) formed in the correspondingsecond pinion shaft 382. Furthermore, from thefirst plate member 51, a plurality of securingportions 59 that are each fitted (snap-fastened) into the center hole of thecarrier cover 42 of theplanetary carrier 40 extend toward the carrier cover 42 (right side inFIG. 6 ). - The
second plate member 52 has aninclined wall portion 54 formed in an annular shape along the inner periphery thereof, Theinclined wall portion 54 protrudes toward the cancelplate 204 and is inclined so as to be closer to the axis as being closer to the cancelplate 204. When the first and thesecond plate members walls 53 of thefirst plate member 51 and theinclined wall portion 54 of thesecond plate member 52. Furthermore, the first and thesecond plate members oil collecting portion 500 and also define anannular oil passage 510 that extends in the radial direction. The hydraulic-oil collecting portion 500, theoil passage 55 a of each of the firsttubular portions 55, and theoil passage 57 a of each of the secondtubular portions 57 communicate with each other through theoil passage 510. - In the present embodiment, as shown in
FIG. 3 , theoil receiver 50 is disposed between thecarrier cover 42 of theplanetary carrier 40 and the cancelplate 204 of the clutch C2. Accordingly, when theplanetary carrier 40 that rotates during operation of theautomatic transmission 25 moves in the axial direction of the input shaft, the outer peripheral portion of thesecond plate member 52 constituting theoil receiver 50 may come into sliding contact with a portion of the adjacent cancelplate 204. In view of this, on thesecond plate member 52, a sliding-contact surface 56 having a smooth annular shape is formed so as to surround theinclined wall portion 54, Furthermore, on the sliding-contact surface 56, a plurality of (eight in the present embodiment)oil grooves 58 are formed at intervals in the circumferential direction. Theinclined wall portion 54 is provided with a plurality of (eight in the present embodiment)notches 54 a through which the hydraulic-oil collecting portion 500 and the area on the sliding-contact surface 56 side communicate with each other at intervals in the circumferential direction. -
FIG. 7 is a front view of theoil receiver 50 when viewed from the sliding-contact surface 56 side. As shown inFIG. 7 , each of theoil grooves 58 is formed on the sliding-contact surface 56 such that the inner peripheral end 58 i thereof communicates with thenotch 54 a and theoil groove 58 is open at the outer periphery of the sliding-contact surface 56, and also the outer peripheral end 58 o thereof is positioned on the downstream side of the inner peripheral end 58 i in the main rotation direction of theplanetary carrier 40, i.e., the rotation direction (see the direction of the arrow inFIG. 8 ) when the vehicle moves forward. In the present embodiment, each of theoil grooves 58 extends spirally (in a substantially arc-shaped manner) along the main rotation direction of theplanetary carrier 40, i.e., in such a manner that a central portion between the inner peripheral end 58 i and the outer peripheral end 58 o is positioned closer to the outer periphery of the sliding-contact surface 56 than to the inner periphery thereof. As shown inFIG. 8 toFIG. 10 , each of theoil grooves 58 has a firstbottom surface 581 that is positioned on the upstream side in the main rotation direction (see the direction of the arrow in the figures) of theplanetary carrier 40 and a secondbottom surface 582 that is positioned on the downstream side in the main rotation direction. - As shown in
FIG. 9 , at the inner peripheral end 58 i, the cross-sectional shape of theoil groove 58 is a right triangle, and the inclination angle θ1 (angle measured counterclockwise from the sliding-contact surface 56 in the figure) of the firstbottom surface 581 with respect to the sliding-contact surface 56 is set at 90°. As can be seen inFIG. 10 , at the outer peripheral end 58 o, the cross-sectional shape of theoil groove 58 is an isosceles triangle, and the inclination angle θ1 of the firstbottom surface 581 with respect to the sliding-contact surface 56 and the inclination angle θ2 (angle measured clockwise from the sliding-contact surface 56 in the figure) of the secondbottom surface 582 with respect to the sliding-contact surface 56 are set at the same value that is relatively small. As shown inFIG. 8 toFIG. 10 , each of theoil grooves 58 is formed such that the inclination angle θ1 of the firstbottom surface 581 with respect to the sliding-contact surface 56 gradually decreases from the inner peripheral end 58 i toward the outer peripheral end 58 o as indicated by the dashed lines in the figure and the width of the secondbottom surface 582 in the circumferential direction accordingly narrows. Consequently, the depth of each of theoil grooves 58 gradually decreases from the inner peripheral end 58 i toward the outerperipheral end 580. - Next, a circulation state of hydraulic oil as a lubricating medium around the clutch C2 and the Ravigneaux type second
planetary gear mechanism 35 of theautomatic transmission 25 described above will be explained. - During operation of the
automatic transmission 25, to the first and the second sun gears 36 a and 36 b of the secondplanetary gear mechanism 35 and bearings disposed around these sun gears, hydraulic oil as a lubricating medium is supplied through an oil passage, for example, formed in theinput shaft 26. The hydraulic oil supplied to thefirst sun gear 36 a and the bearings, for example, lubricates and cools meshing portions between thefirst sun gear 36 a and the short pinion gears 38 a and the bearings, and then flow out from meshing portions between gear teeth, bearings, gaps between thefirst sun gear 36 a and the long pinion gears 38 b, for example. The hydraulic oil partially flows into (is collected by) the hydraulic-oil collecting portion 500 of theoil receiver 50 attached to theplanetary carrier 40 of the secondplanetary gear mechanism 35. - The hydraulic oil partially collected by the hydraulic-
oil collecting portion 500 of theoil receiver 50 flows into theoil passages 55 a of the firsttubular portions 55 and theoil passages 57 a of the secondtubular portions 57 through theoil passage 510 by the action of centrifugal force. Furthermore, the hydraulic oil from the hydraulic-oil collecting portion 500 flows into theneedle bearings 383 of the short pinion gears 38 a through the in-shaftaxial oil passages 381 a of thefirst pinion shafts 381 and in-shaft radial oil passages (in-shaft oil passages) 381 b communicating therewith, and also flows into theneedle bearings 384 of the long pinion gears 38 b through the in-shaftaxial oil passages 382 a of thesecond pinion shafts 382 and in-shaft radial oil passages (in-shaft oil passages) 382 b communicating therewith. This makes it possible to lubricate and cool theneedle bearings - The hydraulic oil partially flowing through the
needle bearings planetary carrier 40 through the spaces G of thecarrier body 41, The hydraulic oil partially flowing out through the spaces G flows into the vicinity of theseparator plates 201 and thefriction plates 202 of the clutch C2 that are disposed to surround theplanetary carrier 40 to lubricate and cool theseparator plates 201 and thefriction plates 202. In theplanetary carrier 40 of the secondplanetary gear mechanism 35, as described above, therecess 415 r is defined by the inner peripheral surface and the pair of thewall portions 415 w of thebridge portion 415, Therecess 415 r of thebridge portion 415, together with thecarrier cover 42, functions as an oil accumulating portion that stores hydraulic oil scattered from the inside (axis side). Thus, the hydraulic oil scattered from the inside, i.e., the side of short pinion gears 38 a and the long pinion gears 38 b can be stored inside therespective bridge portions 415 so as to be prevented from being excessively discharged outside through the spaces G. - Accordingly, the hydraulic oil stored in the
recesses 415 r of therespective bridge portions 415 can be sufficiently supplied as a lubricating medium through the oil holes 415 h to thefriction plates 202 fitted onto thespline 415 s and theseparator plates 201 disposed adjacently thereto, and thus the clutch C2 can be caused to smoothly operate. In theplanetary carrier 40 of the secondplanetary gear mechanism 35, thebridge portions 415 extend from theshaft support portion 410 of thecarrier body 41 so as to be arranged side by side in the circumferential direction with spaces G therebetween, and the long pinion gears 38 b each having a long length are exposed outside through the spaces G, which makes it possible to reduce the outer diameter (occupied space) around thebridge portions 415, Consequently, while making the compactplanetary carrier 40 of the secondplanetary gear mechanism 35 including the short pinion gears 38 a and the long pinion gears 38 b having axial lengths different from each other, it is possible to sufficiently supply hydraulic oil as a lubricating medium to thefriction plates 202 supported by thebridge portions 415. The bridge portions may extend from thecarrier cover 42, and in this case, thecarrier body 41 may be fixed to the distal ends of the bridge portions. - Meanwhile, the hydraulic oil partially collected by the hydraulic-
oil collecting portion 500 of theoil receiver 50 reaches thenotches 54 a formed on theinclined wall portion 54 of theoil receiver 50, and the hydraulic oil reaching therespective notches 54 a directly and smoothly flows into therespective oil grooves 58. Herein, as described above, each of theoil grooves 58 is formed such that the outer peripheral end 58 o thereof is positioned on the downstream side of the inner peripheral end 58 i in the main rotation direction of theplanetary carrier 40, and extends spirally along the main rotation direction. Thus, the length of each of theoil grooves 58 from the inner peripheral end 58 i to the outer peripheral end 58 o is longer than an oil groove that extends straight in the radial direction. With this configuration, theoil receiver 50 can delay the time at which hydraulic oil flowing into theoil grooves 58 from thenotches 54 a reaches the outer periphery of the sliding-contact surface 56 by the action of centrifugal force generated when theplanetary carrier 40 rotates. The hydraulic oil in therespective oil grooves 58 can be more smoothly fed by the centrifugal force onto the sliding-contact surface 56 on the upstream side of theoil grooves 58 in the rotation direction, i.e., between the sliding-contact surface 56 and the cancelplate 204 of the clutch C2. - In the
oil receiver 50, each of theoil grooves 58 is formed such that the depth thereof gradually decreases from the inner peripheral end 58 i toward the outerperipheral end 580. By increasing the depth of each of theoil grooves 58 on the inner peripheral end 58 i side in this manner, even when the hydraulic oil in theoil groove 58 is fed to an inner peripheral area on the sliding-contact surface 56 by centrifugal force, the hydraulic oil can still remain in theoil groove 58. The hydraulic oil remaining in theoil groove 58 on the inner peripheral end 58 i side can be fed out toward the outer peripheral end 58 o by centrifugal force, and also fed to an outer peripheral area on the sliding-contact surface 56. Furthermore, each of theoil grooves 58 has the firstbottom surface 581 positioned on the upstream side in the main rotation direction of theplanetary carrier 40 and the secondbottom surface 582 positioned on the downstream side in the main rotation direction, and is formed such that the inclination angle θ1 of the firstbottom surface 581 with respect to the sliding-contact surface 56 decreases and the width of the secondbottom surface 582 in the circumferential direction narrows from the inner peripheral end 58 i toward the outerperipheral end 580. This makes it possible to smoothly feed the hydraulic oil in theoil groove 58 on the outer peripheral end 58 o side of theoil groove 58 to an outer peripheral area on the sliding-contact surface 56, and to reduce the amount of oil discharged outside from theoil groove 58 at the outer periphery of the sliding-contact surface 56. - Consequently, even if the sliding-
contact surface 56 of theoil receiver 50 comes into sliding contact with the cancelplate 204 of the clutch C2 when theplanetary carrier 40 that rotates moves in the axial direction, the hydraulic oil as a lubricating medium can be distributed between the sliding-contact surface 56 and the cancelplate 204 in an extremely satisfactory (even) manner. Thus, it is possible to satisfactorily suppress wear, for example, of the sliding-contact surface 56 associated with the sliding contact with the cancelplate 204 to improve the durability of theoil receiver 50. - In the embodiment described above, all of the
oil grooves 58 are open at the outer periphery of the sliding-contact surface 56, but the structure thereof is not limited to this. Specifically, like theoil receiver 50B shown inFIG. 11 andFIG. 12 , at least portions of a plurality ofoil grooves oil grooves 58B that are disposed alternately with the oil grooves 58 (that are the same as theoil grooves 58 of theoil receiver 50 described above) may be formed so as to be closed on the inner peripheral side with respect to the outer periphery of the sliding-contact surface 56. Each of theoil grooves 58B is formed on the sliding-contact surface 56 such that the inner peripheral end 58 i thereof communicates with thenotch 54 a. Also, the outer peripheral end 58 o thereof is positioned on the downstream side of the inner peripheral end 58 i in the main rotation direction (see the direction of the arrow inFIG. 11 ) of theplanetary carrier 40. Each of theoil grooves 58B extends spirally (in a substantially arc-shaped manner) along the main rotation direction of theplanetary carrier 40. - As can be seen in
FIG. 12 , theoil groove 58B is also formed such that the depth thereof gradually decreases from the inner peripheral end 58 i toward the outerperipheral end 580. Specifically, at the inner peripheral end 58 i, the cross-sectional shape of theoil groove 58B is also a right triangle, and the inclination angle θ1 of the firstbottom surface 581 with respect to the sliding-contact surface 56 is set at 90°. Each of theoil grooves 58B is formed such that the inclination angle θ1 of the firstbottom surface 581 with respect to the sliding-contact surface 56 gradually decreases from the inner peripheral end 58 i toward the outer peripheral end 58 o as indicated by the dashed line inFIG. 12 , and the width of the secondbottom surface 582 in the circumferential direction accordingly narrows. Because each of theoil grooves 58B is closed at the outer peripheral end 58 o, as can be seen inFIG. 12 , at the outer peripheral end 58 o (closed end) of theoil groove 58B, the inclination angle θ1 of the firstbottom surface 581 with respect to the sliding-contact surface 56 and the inclination angle θ2 of the secondbottom surface 582 with respect to the sliding-contact surface 56 are 0°. - By closing at least portions of the
oil grooves contact surface 56 in this manner, the amount of oil discharged outside from theoil grooves contact surface 56 can be reduced, and the hydraulic oil as a lubricating medium can be more satisfactorily distributed between the sliding-contact surface 56 of theoil receiver 50B and the cancelplate 204 disposed adjacently to theplanetary carrier 40. - As described above, a planetary carrier according to an exemplary aspect of the present disclosure is a planetary carrier of a planetary gear including a plurality of first pinion gears and a plurality of second pinion gears having longer axial lengths than those of the first pinion gears, the planetary carrier including: a carrier body including a plurality of first shaft support portions that each support one end of a first pinion shaft inserted into each of the first pinion gears, and also including a plurality of second shaft support portions that are arranged alternately with the first shaft support portions along a circumferential direction and each support one end of a second pinion shaft inserted into each of the second pinion gears; a carrier cover that supports the other end of the first pinion shaft and the other end of the second pinion shaft; and a plurality of bridge portions that extend in an axial direction of the first and the second pinion shafts between the first shaft support portions and the carrier cover, and are arranged side by side in the circumferential direction with spaces therebetween. The second pinion gears are disposed so as to be at least partially located in the spaces between the adjacent bridge portions. An outer peripheral surface of each of the bridge portions is provided with a spline onto which a friction engagement plate constituting a friction engagement element is fitted. An inner peripheral surface of each of the bridge portions is provided with a pair of wall portions that extend in the axial direction along side edges on both sides of the bridge portion and protrude radially inward. Each of the bridge portions is provided with a plurality of oil holes through which an inside and an outside of the bridge portion communicate with each other.
- In other words, the planetary carrier according to the present disclosure is structured with the carrier body and the carrier cover that support the first pinion shafts inserted into the first pinion gears and the second pinion shafts inserted into the second pinion gears. The carrier body includes the first shaft support portions that each support one end of each of the first pinion shafts inserted into each of the first pinion gears, and also includes the second shaft support portions that are arranged alternately with the first shaft support portions along the circumferential direction and each support one end of each of the second pinion shafts inserted into each of the second pinion gears. The carrier cover supports the other end of each of the first pinion shafts and the other end of each of the second pinion shafts. Furthermore, between the first shaft support portions and the carrier cover, the bridge portions are provided that extend in the axial direction of the first and the second pinion shafts and are arranged side by side in the circumferential direction with spaces therebetween. The second pinion gears are disposed so as to be at least partially located in the spaces between the adjacent bridge portions. Furthermore, in this planetary carrier, the outer peripheral surface of each of the bridge portions is provided with the spline onto which the friction engagement plate constituting the friction engagement element is fitted. The inner peripheral surface of each of the bridge portions is provided with the pair of wall portions that extend in the axial direction along the side edges on both sides of the bridge portion and protrude radially inward. Each of the bridge portions is provided with the oil holes through which the inside and the outside of the bridge portion communicate with each other.
- In this manner, the bridge portions are provided so as to be arranged side by side in the circumferential direction between the first shaft support portions of the carrier body and the carrier cover, and the second pinion gears are disposed so as to be at least partially located in the spaces between the adjacent bridge portions, whereby the outer diameter (occupied space) of the planetary carrier around the bridge portions can be reduced. In this planetary carrier, the carrier cover and the inner peripheral surface and the pair of wall portions of each of the bridge portions define an oil accumulating portion that stores hydraulic oil scattered from the inside (axis side). Thus, the hydraulic oil scattered from the inside can be stored inside the bridge portions so as to be prevented from being discharged outside through the spaces, and then the hydraulic oil as a lubricating medium can be supplied through the oil holes to the friction engagement plate fitted onto the spline. Consequently, while making the compact planetary carrier of the planetary gear including the first and the second pinion gears having axial lengths different from each other, it is possible to sufficiently supply the hydraulic oil as a lubricating medium to the friction engagement plates supported by the bridge portions.
- The first shaft support portions of the carrier body may be a plurality of thick portions that are arranged side by side in the circumferential direction with spaces between the bridge portions, the second shaft support portions may be a plurality of thin portions that are molded integrally with the thick portions, and the first pinion gears may be disposed between the carrier cover and the thick portions and radially inward of the bridge portions. In this manner, the shaft support portions are provided with the thick portions and, from each of the thick portions, the bridge portion extends together with the thick portion, which makes it possible to appropriately increase the torsional rigidity of the carrier body, and consequently the torsional rigidity of the planetary carrier.
- Furthermore, the first pinion gears and the second pinion gears may mesh with each other, and the planetary gear may be a Ravigneaux type planetary gear having a first sun gear meshing with the first pinion gears, a second sun gear meshing with the second pinion gears, and a ring gear meshing with the second pinion gears. However, the planetary gear including the planetary carrier according to the present disclosure is not limited to the Ravigneaux type planetary gear if the planetary gear includes the first and the second pinion gears having axial lengths different from each other.
- The bridge portions may extend from the respective first shaft support portions, and the carrier cover may be fixed to distal ends of the bridge portions. However, the bridge portions may extend from the carrier cover, and the carrier body may be fixed to the distal ends of the bridge portions.
- Furthermore, the second pinion gears may be partially located within a range of radial thickness of the bridge portions.
- The present disclosure is not limited to the embodiment described above and, needless to say, various changes may be made without departing from the scope of the present disclosure. Furthermore, the mode for carrying out the disclosure described above is merely one specific mode of the disclosure described only in the “SUMMARY”, and does not limit the elements of the disclosure described in the “SUMMARY”.
- The present disclosure is applicable to the manufacturing industry, for example, of planetary gears and transmissions including the planetary gears, for example.
Claims (12)
1. A planetary carrier of a planetary gear including a plurality of first pinion gears and a plurality of second pinion gears having longer axial lengths than those of the first pinion gears, the planetary carrier comprising:
a carrier body including:
a plurality of first shaft support portions that each support one end of a first pinion shaft inserted into each of the first pinion gears, and
a plurality of second shaft support portions that are arranged alternately with the first shaft support portions along a circumferential direction and each support one end of a second pinion shaft inserted into each of the second pinion gears;
a carrier cover that supports the other end of the first pinion shaft and the other end of the second pinion shaft; and
a plurality of bridge portions that extend in an axial direction of the first and the second pinion shafts between the first shaft support portions and the carrier cover, and are arranged side by side in the circumferential direction with spaces between the bridge portions, wherein
the second pinion gears are disposed so as to be at least partially located in the spaces between the adjacent bridge portions,
an outer peripheral surface of each of the bridge portions is provided with a spline onto which a friction engagement plate constituting a friction engagement element is fitted,
an inner peripheral surface of each of the bridge portions is provided with a pair of wall portions that extend in the axial direction along side edges on both sides of each of the bridge portions and protrude radially inward, and
each of the bridge portions is provided with a plurality of oil holes through which an inside and an outside of each of the bridge portions communicate with each other.
2. The planetary carrier according to claim 1 , wherein:
the first shaft support portions of the carrier body are a plurality of thick portions that are arranged side by side in the circumferential direction with the spaces between the bridge portions, and the second shaft support portions are thin portions that are molded integrally with the thick portions, and
the first pinion gears are disposed between the carrier cover and the first shaft support portions and radially inward of the bridge portions.
3. The planetary carrier according to claim 2 , wherein
the first pinion gears and the second pinion gears mesh with each other, and
the planetary gear is a Ravigneaux type planetary gear having a first sun gear meshing with the first pinion gears, a second sun gear meshing with the second pinion gears, and a ring gear meshing with the second pinion gears.
4. The planetary carrier according to claim 3 , wherein
the bridge portions extend from the respective first shaft support portions, and
the carrier cover is fixed to distal ends of the bridge portions.
5. The planetary carrier according to claim 4 , wherein:
the second pinion gears are partially located within a range of radial thickness of the bridge portions.
6. The planetary carrier according to claim 1 , wherein:
the bridge portions extend from the respective first shaft support portions, and
the carrier cover is fixed to distal ends of the bridge portions.
7. The planetary carrier according to claim 6 , wherein:
the second pinion gears are partially located within a range of radial thickness of the bridge portions.
8. The planetary carrier according to claim 1 , wherein:
the second pinion gears are partially located within a range of radial thickness of the bridge portions.
9. The planetary carrier according to claim 2 , wherein:
the bridge portions extend from the respective first shaft support portions, and
the carrier cover is fixed to distal ends of the bridge portions.
10. The planetary carrier according to claim 9 , wherein:
the second pinion gears are partially located within a range of radial thickness of the bridge portions.
11. The planetary carrier according to claim 2 , wherein:
the second pinion gears are partially located within a range of radial thickness of the bridge portions.
12. The planetary carrier according to claim 3 , wherein:
the second pinion gears are partially located within a range of radial thickness of the bridge portions.
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JP2013242953A JP6119575B2 (en) | 2013-11-25 | 2013-11-25 | Planetary carrier |
JP2013-242953 | 2013-11-25 | ||
PCT/JP2014/080617 WO2015076291A1 (en) | 2013-11-25 | 2014-11-19 | Planetary carrier |
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US15/035,260 Active US9784364B2 (en) | 2013-11-25 | 2014-11-19 | Planetary carrier |
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JP (1) | JP6119575B2 (en) |
CN (1) | CN105705838B (en) |
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EP3354940B1 (en) * | 2017-01-30 | 2020-03-04 | Rolls-Royce Deutschland Ltd & Co KG | Planetary gear system and gas turbine engine with a planetary gear system |
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CN108397543B (en) * | 2018-05-11 | 2023-11-14 | 浙江吉利变速器有限公司 | Planetary gear support structure and planetary gear mechanism with same |
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JP4910606B2 (en) | 2006-09-29 | 2012-04-04 | アイシン・エィ・ダブリュ株式会社 | Planetary gear unit |
JP2008121808A (en) | 2006-11-13 | 2008-05-29 | Aisin Aw Co Ltd | Automatic transmission |
JP5125761B2 (en) * | 2008-05-23 | 2013-01-23 | 株式会社ジェイテクト | Planetary carrier, planetary gear mechanism, and vehicle differential equipped with these |
US9157521B2 (en) | 2011-12-16 | 2015-10-13 | Aisin Aw Co., Ltd. | Planetary carrier |
JP6102208B2 (en) | 2012-11-19 | 2017-03-29 | アイシン・エィ・ダブリュ株式会社 | Automatic transmission |
-
2013
- 2013-11-25 JP JP2013242953A patent/JP6119575B2/en active Active
-
2014
- 2014-11-19 WO PCT/JP2014/080617 patent/WO2015076291A1/en active Application Filing
- 2014-11-19 US US15/035,260 patent/US9784364B2/en active Active
- 2014-11-19 CN CN201480061244.9A patent/CN105705838B/en active Active
- 2014-11-19 DE DE112014004547.0T patent/DE112014004547T5/en not_active Withdrawn
Patent Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
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US20030100399A1 (en) * | 2000-10-23 | 2003-05-29 | Masahiro Hayabuchi | Planetary gear set |
US20100105515A1 (en) * | 2008-10-24 | 2010-04-29 | Goleski Gregory D | Planet pinion carrier for a gearset |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20180058511A1 (en) * | 2015-03-31 | 2018-03-01 | Aisin Aw Co., Ltd. | Speed change device |
US10663011B2 (en) * | 2015-03-31 | 2020-05-26 | Aisin Aw Co., Ltd. | Speed change device |
US10794466B2 (en) | 2016-08-10 | 2020-10-06 | Kawasaki Jukogyo Kabushiki Kaisha | Planetary gear device |
US10428928B2 (en) * | 2017-03-24 | 2019-10-01 | Hamilton Sundstrand Corporation | Lubrication system for high speed gearbox operating in zero gravity |
Also Published As
Publication number | Publication date |
---|---|
JP6119575B2 (en) | 2017-04-26 |
DE112014004547T5 (en) | 2016-07-21 |
US9784364B2 (en) | 2017-10-10 |
WO2015076291A1 (en) | 2015-05-28 |
CN105705838A (en) | 2016-06-22 |
CN105705838B (en) | 2018-03-06 |
JP2015102161A (en) | 2015-06-04 |
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